Machine-tool control



May 1945- c. JOHNSON 2,399,806

MACHINE TOOL CONTROL Original Filed March 2O 1941 7 Sheets-Sheet 1 1 ,1 '1, IIIIIIII lull!- .Snventor CLARENCE JOHNS-ON May 7, 1946.

' c. JOHNSON 2,399,806

MACHINE TOOL- CONTROL Original Filed March 20,- 1941 7 Sheeis-Sheet 2 Inventor CLARENCE JOHNSON May 7, 1946. c. JOHNSON 2,399,806

MACHINE TOOL CONTROL Original Filed March 20, 1941 7 Sheets-Sheet 3 "4' ugh Z3 m iim'laiai fil JR r1 pl 56 A Inventor CLARENCE JOHNSON FIG. 5 v f hJwM May 7, 1946. c.- JOHNSON MACHINE TOOL CONTROL Original Filed March 20 1941 as Q o Q 0 1' s3 *Mfls as 44 43 I o I: H o g o 0 .4 i: 1 :11: 92A

7 s I 5 92 l L v a) L Iglwerltor FIG. 7 CLARENCE JOHNSON 7 Sheets-She et 4 Y 1946; Q c. JOHNSON 2,399,806

MACHINE TOOL CONTROL I Original Filed March 20 1941 7 Sheets-Sheet 5 5 n. a. D m

FIG. 9

CLARENCE JOHNSON Ka ma/AW y 1945- c. JOHNSON 2,399,806

MACHINE TOOL CONTROL Original Filed March 20 1941 7 Sheets-Sheet 6 F m i use [I88 I u %/2ao Q Inventor 1 CLARENCE JOHNSON B E :60 AIR /far S UPPLY I attorney ing machines and the.

Patented May 7, 1946 MACHINE-TOOL CONTROL Clarence Johnson, South Euclid, Ohio, assignor to Bailey Meter Company, a corporation of Delaware - Original application March 20, 1941, Serlal No.

384,375, now Patent No. 2,372,426, dated-March 27, 1945. Divided and this application June 17, 1943, Serial No. 491,162

'1 Claims.

This invention relates to duplicators for controlling the operation of a machine tool so that it forms a work piece to a. contour or configuration determined by a template, pattern, or cam.

One of the objects of my invention is to improve the. sensitivity of duplicators of the typ described, and thereby increase the accuracy with which the work piece is formed.

A further object of my invention is to provide a duplicator of materially simpler construction than those now available.

A further object of my invention is to provide a duplicator employing no moving parts in the feeler mechanism scanning the template, patter or cam.

in accordance with my invention the template, pattern or cam for producing the desired configuration of the work piece is scanned by a j t of fluid issuing from a nozzle, so that variations in the shape of the template, pattern or cam cause corresponding changes in the rate at which fluid is'discharged from the nozzle, which changes in turn control the relative movement of the tool and work piece.

Further, in accordance with my invention the changes in the rate at which fluid is discharged from the nozzle effect corresponding variations in the pressure of the fluid inthe nomle, .which latter variations are used to control the relative positioning of the tool and work piece.

Further, in accordance with my invention the changes in fluid pressure control the relative posii tioning of the tool and work piece through a hyspecific types of machine tools. Further applications and modifications of my invention will be readily apparent.

draulic relay and servo-motor, to the end that ample power is available for accurately positioning the tool relative to the work piece.

Further, in accordance withmy invention-the relative rates of movement between the tool and work piece in two directions are simultaneously controlled. so that the rate of feed of the tool remains substantially constant regardless of changes in contour of the template, pattern or cam. I I I 1 Further, in accordance with my invention cope-- rate and, independent means are provided for In the drawings:

Fig. 1 is a side elevation elevation of a vertical milling machine illustrating the application of my invention thereto.

Fig. 3 is a sectional view taken along the line '3-3. of Figs. 1 and 2 in .the direction of the arrows.

Fig. 4 illustrates a scanning mechanism.

Fig. 5 is a cross-sectional view of a pilot valve for controlling the flow oi fluid to and from a hydraulic servo-motor for regulating the relative feed of the tool and work piece.

Fig. 6 illustrates diagrammatically a modified form of fluid pressure system.

Fig. 7 is a side elevation and Fig. 8 is a plan view of an engine lathe showing the application 0! my invention thereto.

Fig. 9 is a plan view of an engine lathe illusmodified form of nozzle trating the application of a, modified form of my invention thereto.

Fig. 10 illustrates diagrammatically the various circuits employed in the embodiment of'my invention shown in Fig. 10.

Fig. 11 is a cross-sectional view of one form of pilot valve employed in the power unit.

Fig. 12 is an elevation view of a sleeve element of the pilot valve shown in Fig. 11. Fig. 13 is an end view of a, bearing element of the pilot valve shown in Fig. 11.

Fig. 14 is an elevation view and Fig. 15 a crosssection view of another form of pilot valve which in the power unit. Figs. 1, 2 and 3, I therein may be incorporated Referring now to show a vertical milling machine having a column I, a work table 2, and-a rotatable form milling cutter The work table 2 is carried in a saddle 4 mounted on horizontal guide ways 5 carried by a knee 8 which is supported in vertical guide ways I formed on the column I. l A micrometer hand controlling the rate of relative movement between tool and work piece in each direction.

Obviously, a duplicator of the type forming the subject matter or my invention may be employed with machinetools 01 various types. such as millns machines, lathes, slotters. maners,'die-sink like inwhich the relativeieedbetween the tool; and-work may be suitably controlled. By way of example I will illustrate 'and describe my invention at applied to a few 'slon'goneormore wheel 8 is provided for positioning the saddle 4 along the guide ways 5. A similar hand wheel I is provided for positioning the knee I along the vertical guide ways I. The work I table 2 is mounted on a horizontal guideway ll formed in the saddle l and is positionable relative thereto hyaleadscrew ll. Thecutterlissecuredtoa spindle II rotated by a motor ll, which may be vtin-theiadapted to position the worisv table 2 I oi the guideways as well known.

At llisshown atypicalworkpteeecomistins of a. concave 10min: of more or-less elliptical and Fig. 2 is a front I shape and-in rough form having a raised blank face extending around its entire periphery. The

Because of the nature of the machining operation to be performed the fixture i is mounted on a circular table I! secured to the work table 2 and rotatable at desired speed by the motor I 3 through suitable reducing gears and shafting (not shown). The machining of the work piece I4 is completed in one revolution of the circular table II, during the revolution the work piece being moved relative to the cutter 3 to accurately profile the male flange by means new to be described.

The fixture 15 has a horizontally extending skirt l9 forming a cam or template, the contour of which is formed to produce the desired contour of the raised portion of the flange on the work piece 14. A raised barrier 20 is preferably employed to hold chips cut from the work piece from scattering.

Fastened to the column i is an arm 2| in which is journaled a nozzle 22. Secured to the nozzle is an extension 23 which pivotally supports a follower 24 having a projection 25 urged against the cam or template it by a spring 26. The nozzle 22 is preferably resiliently journaled in the arm 20 by means of spaced collars 2! and spring 28, which provide for lateral movements, thereby preventing injury to the nozzle in the event that the follower 24 is inadvertently jammed against it.

The nozzle 22 is connected to a suitable source of pressure fluid (not shown), such as compressed air, by a flexible tube 29 in which is inserted an orifice or other partial restriction 30. Normally therefore a jet of fluid is continuously discharged from the port 3| against the follower 2%, which acts as a valve member for the port, its movements toward and away from the port governing the rate of discharge of fiuid therefrom. That is to say. when the follower 24 is positioned to the left, or closer to the port 3!, as shown in Fig. 3, the rate of discharge from the port is decreased, whereas when the follower 24 is positioned to the right, Or away from the port, the rate of discharge from the nozzle increases. Such changes in the rate of discharge from the port effect corresponding changes in thepressure of the fluid within the nozzle, a decrease in the rate of discharge effecting an increase in the pressure of the fluid within the nozzle, whereas an increase in the rate of discharge effects a correspondingdecrease in fluid pressure. I

As the'template I9 and the work piece l4 are rotated by the circular table II the follower 24 will be positioned toward and away from the port 3| in accordance with changes in the configuration of the template. Such positioning of the follower 24 efiects' changes in thepressure of the fluid within the nozzle 22. These pressure variations are effective for positioning the work table 2, to return thesfollower 24 to the normal distance from the port 3|. Inasmuch as in the embodiment of my invention illustrated in Figs.

1, 2 and 3 the cutter 3 is stationary, as is also the nozzle 22, it follows that if the work table 2 is positioned to maintain a normal distance between the follower 24 and port 3| the work piece l4 will upon completion of the machining operation have a configuration determined by the configuration of the template l9.

Inasmuch as the circular table I! rotates, whereas the work piece may have a shape other than circular, and furthermore may not be concentrically located on the table with respect to the center of rotation thereof, it follows that the periphery of the work piece will not be a duplicate of that of the template 19. The proper contour of the template to give the desired shape to the work piece may be determined, as evident to-those skilled in the art, by calculation or graphically.

The pattern or template has a shape corresponding to the desired path of movement of the tool to produce the desired finished work piece. By corresponding is'meant that not only is the pattern or template the same shape as the desired work piece, either in greater or smaller proportions thereto; but also that the pattern or template is in any desired distorted shape to compensate for characteristics of the machine. While the pattern or template must correspond to the desired work piece, it is not necessarily identical in contour, and, therefore, the term correspond implies that the pattern or template is purposely designed to result in the desired contour of the work piece to be produced.

Changes in the shape and size of the projection 25 relative to that of the cutter 3 will also modify the shape of the template as necessary to produce a desired shape of the work piece it. In some instances the design of the template it is somewhat simplified by having the projection 25 the same shape and size as the cutter 3i, and there fore I usually find it desirable to employ the construction shown in Fig. 3. However, in some instances it may be preferable to employ the construction shown in Fig. 4. As shown, the follower 24 and projection 25 are eliminated. The nozzle 22 is located immediately adjacent the template I9 so that the template itself acts as the valve member for the port 3!. Other than this the construction and operation will be as described with reference to Fig. 3.

Pressures established within the nozzle 22 are transmitted through a flexible tube 33 to a relay within a protecting housing 33A and shown in cross section in Fig, 5. The tube 33 connects with the interior of a bellows 32 secured to a wall of the housing 33A. The force produced by the fluid pressure acts against the lower or free head of the bellows and is opposed by the inherent resiliency of the bellows and an elliptical spring 35. The free head of the bellows will therefore assume a position corresponding to the magnitude of the fluid pressure. Movements of the lower head of the bellows position a movable valve member 36A of a hydraulic pilot valve 36 to control the flow of hydraulic fluid to and from a servo-motor 38 having a piston 31 operating the lead screw ll through-a rack 39, spur gears 40. and a final gear 4| which is splined to the lead screw to permit relative axial movement.

Assuming'now that the normal distance exists between the port 3| and follower 24 a definite pressure will exist within the bellows 32, which by adjustment of the spring 35 will cause the valve member 36A to assume a neutral position, i. e. aposition in which no hydraulic fluid passes between the pilot valve 36 and servo: motor 33. If now thefollower 24 moves toward the port 3| the pressure :within the bellows 32 will increase, causing a'downward positioning of the valve member 35A, a e of hydraulic fluid between the pilot valve 35 and servo-motor 38 causing the piston 31 to move the work table 2 in a direction to restore the port 3| and follower 24 to normal distance. Upon a decrease in fluid pressure within the bellows 32 the servo-motor 38 will position the work tabl 2 in opposite direction, thereby positioning the follower 24 toward the port 22 until normal distance is restored. It

'is apparent that by proper shaping of the template IS the follower 24 may be moved toward l1 revolves to eilect corresponding movements. of the work table 2 relative to the cutter 3 to effect accurate shaping of the work piece l4.

Hydraulic fluid, such as oil, used in positioning the piston 31 of the servo-motor 38 may be pumped by any suitable means, such as the oil pump 43 driven by a motor 44. The pump 42 is provided with an inlet pipe 45 extending into an oil reservoir 46, and a discharge pipe 41 which is connected to the inlet port 60 of the pilot valve 35. Hydraulic fluid returned from the servomotor 38 to the pilot valve is passed to the reservoir 45 through exhaust pipes 48 and 49.

The pilot valve 36 is provided with outlet ports 50 and 5|. with one side of the piston 31 through a pipe 52, and the latter in communication with the opposite side of the piston through a pipe 53. Downward positioning of the valve member 35A connects the outlet port 50 to the pump-43 and the outlet port 5| with the exhaust pipe 49, whereas upward positioning of the valve member connects the outlet pipe 5| with the pump 43- and the outlet port 50 with the exhaust port 48.

The movable valve member 36A is provided with sealing glands 55 and 55, which are of sub- The former being in communication and away from the port 3| as the circular table stantially the same diameter as the passageway 51 extending longitudinally through the pilot valve. Oil from the pump 43 is admitted under pressure through pipe 41. to the inlet port ill ,which is in the form of an annular chamber.

The port BI isvin communication with the possageway 51 through a plurality of equally spaced upper V-ports II and a similar plurality of lower V-ports 52. With the valve member 36A in the neutral position, that is in the position occupied 1 when thefollower 24 is the normaldistance from the port 3|, then aland 84 restricts cominunication between V-ports i2 and outlet port 50. Likewise a land 35 restricts communication between V-ports 52 and outlet port 5|. When, however,

the valve member 35A is positioned downwardly,

for example, the V-ports 5| are partially uncoveredso that communication is established between the inlet pipe 41 and the outlet port 50. The area of the uncovered. V-ports 5| depends upon the displacement of the valve member 36A from the neutral position, and accordingly the flow-oi oil from the inlet pipe 41 to the outlet port '50 will vary depending upon the displacement of Conversely upon upward posithe valve member. tioning pf the valve member 33A from the neutral position a portion of, the V-ports 82 will be uncovered, thereby permitting a proportionate flow of pressure fluid from the inlet;'pipe 41 to the outlet port 5! Also carried by the valve member "A are lands 66 and 61 cooperating with spaced V-ports l and tablishes communication between the inlet pipe 41 and outlet port 50, communication is likewise established between the outlet port 5| and exhaust pipe 48. Pressure fluid is thus transmitted through pipe 52 to one side of the piston 31 and simultaneously withdrawn from the opposite side of the piston through pipe 53 to exhaust port 49. Upward positioning of the valve member 36A from the neutral position results in opposite action, in this instance pressure fluid being transmitted from inlet pipe 41, pipe 53, to one side of piston 31. Pressure fluid issimultaneously withdrawn from the opposite side of piston 31 through pipe 52 to outlet port 50, and thence to exhaust pipe 48. It will be noted that whenever the valve member 35A is in other than the neutral posivtion, thepiston 31 will continue to move in prefrom the normal position relative to the port 3|.

If a sudden change in contour of template I! occurs, the table 2 will be rapidly positioned but upon a relatively slow rate of change in the contour of the template a correspondingly slow change in position of the table 2 will occur. Thus the pilot valve 35 will cause the work piece to be accurately positioned relative to the cutter without overshooting or hunting.

Preferably the sealing lands 55 and 56 are of substantially the same diameter as the passageway 51, thereby preventing material leakage of oil. The lands 64, 65, 66 and 61 are however of a somewhat less diameter than the passageway 51, thereby preventing undue friction and permitting the member 35A to be freely positioned in the passageway. Th pressure transmitted from the inlet pipe 41 to outlet ports 50 and 5|, with the member 36A in neutral position because the lands 84 and 65 may be of somewhat less diameter than the passageway, will not affect the accuracy with which the piston 31 is positioned for such pressures will be equal and act in opposite. direction on the piston 31. The system willstabilize with the pilot slightly oil center to balance total pressures rather than unit pressures as would be the case with a construction where the piston rod extends through both ends of the cylinder. 1 It will further be noted that the-flows into and out due to the equal areas of lands 54, 65, 56 and 61 6! respectively torontrol the flow of pressure j fluid from theoutlet port II to the exhaust pipe 48, and from the outlet port II to the exhaust pipe 43. It will be noted that'upon downward positioning of the valve member "A, which esso that no reaction exists due to the resultant of the oil pressures acting in an upward or downward direction.

While in general I have found it preferable to operate the table 2 or comparable device indirectly from the fluid pressures established within the nozzle 22 by means of a hydraulic relay, in some instances where a relatively light machining operation is being performed, or an extreme degree of accuracy is not required. I have found it possible to dispense with the hydraulic relay s stem and employ in its stead a pneumatic relay systemasshowninl igfi.

Therein I show fluid pressure, such as compressed air,transmitted from the pipe 29 ahead of the orifice 30 to a pilot valve 10 by a. pipe 1|. The pilot 1. shown in cross-section may be so I face plate SI, and tailstock 82.

constructed that downward positioning of the movable valve member I2 permits pressure fluid to be transmitted to one side of the piston 31 and simultaneously exhausts pressure fluid from the opposite side of the piston 31. Conversely upon upward positioning of the member I2 reverse operation of the piston 31 will occur. When the normal distance exists between port 3I and template I9 the member I2 is positioned so that the lands thereon are adjacent the outlet ports leading to the servo-motor 38.

In the embodiments'of my invention so far deis of importance and which is controlled by my invention. v

Referring to Figs. 7 and 8 I therein show a typical engine lathe having a bed 89, rotatable It is further provided with a carriage 83 movable on guideways 84, 85 longitudinally alon the bed 80. Normally the longitudinal movement of the carriage is controlled by a lead screw 86, which may be driven by any suitable source of power (not shown) at any desired speed by means of suitable reducing ears (not shown).

Mounted on the carriage B3 is a cross-slide Bl carrying a tool holder and tool 81A which by way of example I have shown as forming a work piece 88 into general irregular conical form. In the embodiment of my-invention shown the transverse motion of the cross-slide 81 is automatically controlled so that the work piece 98 is formed to correspond in shape to a template 89, which is secured to the bed 80 of the lathe by suitable clamping means 96.

The system for positioning the tool 87A relative to the work piece 38 is substantially the same as that described for positioning the cutter 3 relative to the work piece l4. Nozzle 22 is resiliently mounted in an arm 9| secured to the cross-slide 81. The projection 25 of the follower 24 bears against the edge of the template 89, which has a contour to which the work piece 88 is to be shaped. Pressures established in the nozzle 22 are transmitted to the relay 33A, which in turn acts to control the positioning of the piston 31 in servo-motor 33. Positioning of the piston 31 controls the transverse positioning of tlge tool 87 through a rack 39 and suitable gears 9 A.

In order that the servo-motor 3B, relay 33A and associated apparatus may move with the 83 at desired speed by any suitable source of power as heretofore described.

In Fig. 9, I show a modified form of my invention applied to an engine lathe I50 similar to the lathe illustrated in Figs. 7 and 8. In Fig. 10 the control and operating circuits for the embodiment of my invention illustrated in Fig. 9 are shown diagrammatically.

Referring to Figs. 9 and 10 the carriage I5I is arranged to be positioned longitudinally along the lathe I50 by a servo-motor I52 having a piston rod I53 operatively connected to the carriage. A cross-slide I54 mounted on the carriage I-5I is positioned transversely by means of a similar servo-motor I55 secured to and movable with the carriage I5I. In the embodiment of my invention illustrated in Fig. 9 the tool I54A carried by the cross-slide I54 is positioned to form a work piece I56 to conform with the shape of a pattern or template I51.

As the carriage I 5| is positioned along the lathe by the servo-motor I52 transverse changes in the profile of the pattern I5! efiect corresponding changes in the relative positions of a pivoted follower or feeler I58 and nozzle I59. The nozzle I59 is supplied with fluid under pressure, such as compressed air, from a source (not shown), through a shut-off valve IBII, a reducing valve I 60A, a stabilizing volume tank I6I and a suitable resistance such as an orifice I62. As in the embodiments-oi my invention previously described, compressed air .is continuously discharged through the nozzle I59 to the atmosphere and changes ,in the position of the feeler able valve member I66 of a pilot valve I61.

I58 relative to the nozzle I59 cause changes in the pressure within the pipe I63 connecting the nozzle I59 to the orifice I62. Variations in pressure within the pipe I63 are transmitted through a pipe I-64 to an expansible contractible chamber such as a bellows I65 positioning the mov- The pilot valve I61 controls the flow of hydraulic fluid to and from a servo-motor I 55.

When the profile of the pattern I5! is parallel to the line of travel of the carriage I5I a certain distance will exist between the nozzle I59 and feeler I58. When this distance, which for convenience I call the normal distance, exists a sufficient pressure is maintained within the bel lows I65 to hold the movable valve member IE5 in a neutral position so that hydraulic fluid is transmitted neither tonor from the servo-motor I and the cross-slide I54 remains stationary relative to the carriage I 5I. Assuming however by way of example that the feeler I58 moves toward the nozzle I59, the pressure within the pipe cross-slide GI longitudinally along the lathe they are shown mounted on a truck 92 provided with flanged wheels 93 riding on rails 94. The truck 92 is secured to the carriage 83 so that the servomotor is maintained at proper operating distance from the cross-slide 81.

In operation, as the template 8! changes in shape corresponding variations in pressure within the nozzle 22 occur, which efiect transverse operation of the cross-slide 81 to maintain the follower 24 at normal distance from the port 3|. Simultaneously, the tool 81 is moved transversely so that the work piece 88 assumes the same shape as the template 89. The cross-slide 81 is moved I93 and that transmitted to the bellows I will increase proportionately. Such increase in pres sure will cause the servo-motor I55 to position the cross-slide I54 so that the nozzle I 59 carried thereby moves away from the feeler I58 until normal distance is restored therebetween. The tool I54A also carried by the cross-slide I54 will be moved relative to the work piece I56 a corresponding amount, and hence the latter will be formed to the exact configuration of the pattern or template I51. Hydraulic fluid, such as oil, is supplied the pilot I61 by means of a pump I58 driven by a motor I69.

In Fig. 11 I show the pilot valve I61 in cross section and to larger size. A body member 350 has a cylindrical bore in which are disposed sleeves 35I, 352 and bearing members 353. 354. Caps 355 and 356 screwed to the body 350 hold longitudinally by the feed screw 36 and carriage the sleeves and bearing members in position.

The movable valve member I66, positioned by bellows I65, is provided with lands 351, 363, 353

and .333 of slightly less diameter than the bore in sleeves 35I, 352. Lands 353, 353 control the flow of hydraulic fluid from an inlet port '36I to outletports 362, 363 respectively connected to servo-motor I55. Lands 351, 363 control the flow of hydraulic fluid from outlet ports 362, 363 to waste ports 364, 365 respectively. Downward movement of the valve member I 66 from the neutral position in which it is shown opens inlet port 36I to outlet port. 362 and permits the passage or hydraulic fluid from the pump I63 to the servo-motor I55. Such movement also opens outlet port 363 to waste port 365 so that as a result of such downward positioning of the valve member I66hydraulic fluid is admitted to servomotor I-55 on one side of piston I55A and dis- -ation of the piston I55A in the opposite direction.

Sleeve 35I which is identical with sleeve 352 is shown to larger size in Fig. 12. The inlet port 3 6I consists of a slot 363, whereas the outlet port consists of a plurality of clrcumferentlally spaced holes 361. the inletport 366 and comprises a slot 363. The

sleeve is also provided with spaced collars 363,

3'I 0'serving to properly align the sleeve in the housing 353 and acting to separate the inlet port from the outlet port and the outlet port from the waste port.

In Fig. 13 I show an end view of the bearing member 353, the bearing member 354 being The waste port is similar to mum rate of speed. However, upon a change trol couple comprising the feeler I53'and a nozzle I31. So long as the profile of, the: pattern I51 is parallel to the line of travel of the carriage I5 I the normal distance is maintained between the ieeler I53 and nozzle I31 so that the servo-motor I52 moves the carriage I5I at any desired maxiin theproflle of the pattern I51 the feeler. I53

, will move toward or away from the nozzle I31,

thereby changing the loading pressure established by the latter and acting to slow down the rate of travel of the carriage I5I. Thus it may be said that the control couple comprising the feeler I53 and nozzle I31 acts to limit the maximum departure of the work piece I56 from the shape of the pattern I51. Upon a predetermined departure otthe relative position of the feeler I53 and nozzle I31 from normal the system disidentical therewith. As shown, the end or bearv ing member 353 adjacent the sleeve 35I isconically recessed and provided with a'radial slot 31I which acts to prevent land 351 adhering to 'u the bearing member if positioned upwardly thereagainst.

.The' pilot valve I61 is inherently stableas a displacement "of the valve member I66 from neutral position with consequent flow of hydraulic fluid produces a slight reaction tending to return the movable valve member to the neutralposition. That such reaction exists will be evident from an inspection of the construction shown in Fig. 11 for upon a displacement of the member I66 from neutral position the sole.

unbalanced force is that inthe waste port 364 or 365. This stabilizing reaction may be brought to any value desired by proper design of the waste ports. Also by having the valve member I66 joumaled in bearing members 353, 354 it is possible to have the lands 351, .353, 353 and 333 of slightly less diameterthan the bore through sleeves'35l and 352, thereby reducing friction to a minimum. 1 Further, to reduce friction the sections of the movable valve member I66, journaled in bearing members 353 and 354,

are provided with a plurality of grooves 312,

, thereby preventing pressure building up on one side of the valve member and producing lateral thrust. Such grooves also reduce the leakage which otherwise would exist between the interior and exterior of the pilot valve.

In mechanisms of the type described-it is desirable to modify the rate of relative movement of tool and work piece in one direction whenever closed will stop the carriage I5l, thereby permitting thetool' I54A to be positioned transversely of the axis of the lathe until such normal is reestablished. Preferably and by means hereinafter to be described, the relative positions of the nozzles I53 and I31 are adjustable so that the maximum tolerance between the shape of the work piece I56 and pattern I51 may be brought within any desired limits. Thus the positioning of the nozzle I31 to the left, as shown in Fig. 9, will cause a greater change in air loading pressure for a given change in the'proflle of pattern I51, and thereby cause a greater change in the rate of travel of the carriage I5I.

Referring now particularly to Fig. 10, compressedair. is'supplied to nozzle I31 through an orifice I33 and pipe I33. Variations in pressure withinthe pipe I33 caused by changes in the relative positions of feeler I53 and nozzle I31 are transmitted to an expansible contractible I bellows I33 through the pipe I3l. Changes in pressure within the bellows I33 from that existing when the ieeler I53 is the normal distance away from the nozzle I31 acts to position a valve member I32 of a pilot valve I33. The pilot valve The servo-motor I52 is supplied with oil under pressure from a pump I34 driven by a motor I35. Conveniently the motor I34, pilot valve I33 and associated apparatus may be mounted upon and within a housing I13A. This apparatus forms a power unit. a

The oil after leaving the pump I34 passes through a four-way valve I36, and thence to the servo-motor I52 on one side of the piston I31. As the piston I31 is positioned to the right, as shown in Fig. 10, by the oil from the pump I34, oil is discharged from the servo-motor I52 through a conduit I33, the four-way valve I36, thence through a three-way valve I33 .120 the pilot valve or variable'resistance I33, whence it is discharged into the reservoir formed by the Caps 206, 201 screw-threaded to the body I93 take the end thrust of the bearing members. Oil

exhausted from the servo-motor I52 enters an initial inlet port 208, passes axially upwardly through an intermediate outlet port 209, whence it is transmitted to an intermediate inlet port 2I0 through a suitable connection (diagrammatically shown) 2I I, and thence axially downwardly to a final outlet port 2I2 from which it is exhausted into the oil reservoir.

Within the passageway is disposed the movable valve member I92 having lands 2I3, 214, 215 and s. In the position shown the resistance to fluid flow through the port 209 is at a minimum, as is that through the port 2 I2. Accordingly, the piston I91 and carriage I5I will be positioned at maximum speed. Upon the valve member I92 moving downwardly, due to an increase in pressure within the bellows I90, the resistance to fluid flow through the. outlet port 209 will increase ina'smllch as the land 2I3 will partially close it. This increase in resistance will decrease the flow of fluid from the servomotor I52, thereby decreasing the rate of travel of the piston I91. If the pressure within the bellow I90 increases sufiiciently so that the land 2I3 completely covers the port 209 the piston I91 will completely stop. Likewise upward movement of the movable valve member I92 from the position shown will cause the land We to partially or wholly cover the port 2 I 2, thereby increasing the resistance to fluid flow and slowing down or stopping the piston I91. It is apparent, therefore, that when the pressure within the bellows E90 isthat produced when the feeler I59 is a normal distance from the nozzle E91, the piston I91 will travel at maximum speed, and an increase or decrease in fluid pressure within the bellows I90 caused by a move ment of the feeler $59 toward or away from the .nozzle I31 will cause the piston I01 to slOW down or completely stop if such movement is of sufficient magnitude.

The inlet ports 208 and 2I0 comprise a plurality of circumferentially spaced holes in the sleeves 20I and 202 respectively. The sleeves are recessed adjacent these ports so that oil flows into the passageway formed by the sleeves through all of the holes simultaneously. The outlet ports 209, 2I2 are formed by end slots in the sleeves 20I and 202. Bearing members 204, 205 are provided with one or more slots 204A, 205A which act to equalize the pressures on opposite side of lands 2I3, 2I6. Slot 204A, 205A having a small area offer a high resistance to the flow of oil.

As will be appreciated by those familiar with t e art, it is desirable to have the maximum rate of travel of the carriage I5l adjustable, depending for example upon the contour of the pattern or template I51, the character of the material being machined, etc. Accordingly, I provide the pilot valve I93 with a means for adjusting the minimum resistance to fluid flow. This I accomplish by providing the caps 206 and 201 with opposite threads, so that as they are rotated in the same direction one will move downwardly and the other upwardly. Such positioning will move the bearing members 204, 205 toward or away from each other, causing sleeve members 20I and 202 to likewise move toward or away from each other. Such positioning of the sleeve members will cause the movable valve member I92 to increase or decrease the effective free area of the ports 209, 2I2 when in the neutral position or that position obtaining when normal distance exists between the nozzle I 81 and feeler I58. Conveniently such adjustment may be obtained by providing the cap 206 and 201 with gears 220, 22I meshing with pinions 222, 223 manually rotatable by means of knob 224.

In the embodiment of my invention shown in Figs. 9 and 10, I provide various safety and other devices for facilitating operation. Thus I show connected in the power supply to motors I69, I95 an air pressure failure switch 230 which prevents their operation unless air pressure i available for the nozzles I59, I91.-' Also shown connected in circuit with motor I95 are limit switches 23I and 232 arranged to be operated by a projection 233 carried by the piston rod of servo-motor I52. The switches may be adjusted so that upon the tool reaching either end of pattern I51 motor I95 is deenergized, thereby preventing further travel of the carriage which might result'in damage to the tool or other parts of the lathe. A push button station 234 allows the operator to reenergize motor I95 after the power supply thereto is broken either at switch 23E or 232. Also connected in circuit with motors I69 and I95 are manually operable push buttons 235 and 236 respectively, which affords the operator instantaneous control over the transverse or longitudinal feed of the tool I54A.

As shown in Fig. -9 the tool I54A is arranged to traverse the work piece I58 from left to right. Upon the tool reaching the end of the work piece moto I95 will be deenergized as heretofore described by switch'232 opening. The tool I54A can then be moved transversely away from the work piece I56 by the nozzle I59 and feeler I 58 being manually moved relative to each other, thereby causing the servo-motor I55 to position the cross-slide in proper direction. In order that the tool I54A may be returned to the left end of its travel I provide a hand operable lever 231 for simultaneously operating the four-way valve I96 and three-way valve I99. Thus upon the tool I54A reaching the right end of its travel, switch 23I will open, deenergizing motor I95. The operator would then relatively move feeler I58 and nozzle I59 so that the tool is positioned away from the work. Lever 231 would then be shifted from stop 231A to 231B and imultaneously the circuit to motor I95 closed by means of push button 234. Shifting of lever 231, as shown in Fig. 10, causes pipe I98 to be connected to pump I94 while the connection to servo-motor I52 at the opposite side of piston I91 is connected directly to the oil reservoir formed by housing I10A through three-way valve I99. As full pressure developed by the pump I94 is available for positioning the piston I91 in reverse direction, and by virtue of the fact that the pilot valve I93 is by-passed, the reverse traverse will be made at ahigh speed.

In the event that it is desired to have the tool I54A feed in the reverse direction, that is from left to right, then by disconnecting the lever 231 at 231C from the three-way valve 1" so that movement of the lever adjusts only the tour-way valves I95, then the pump I! will deliver pressure fluid through the pipe ISO to the servo-motor I52, whereas the cylinder of servo-motor I52 on; the opposite side of piston ill will be connected 'to the pilot valve I93. Accordingly, with such an arrangement the operation will be as previously described, except that the tool INA will feed from right to left as viewed in Fig. 9 rather than from left to right.

This application is a division of my copending application Serial No. 384,375 filed in the United States Patent Ofllce on March 20,1941, and now Patent No. 2,372,426, granted March 27, 1945. Certain features of my invention, disclosed but not claimed herein, are disclosed and claimed in .my copending divisional application Serial No.

642,175 flied January 19, 194

While in accordance withthe Patent Statutes I have described certain embodiments of my invention it is evident that such embodiments may be modified in many ways without departing from the spirit and scope or the invention. Such embodiment of my invention as I have chosen to describe should therefore be taken a merely illustrative and not as limiting.

-What I claim as new, and desire to secure by Letters Patent of the United States, is:

v 1. In a machine tool control, a tracer mechanism for producing a control eflect corresponding to the profile of a pattern, an expandable contractible chamber to which the control effect is applied and having a movable portion, and a pilot valve positioned by said movable portion and controlling a fluid flow, said pilot valve so constructed that when the tracer is in a predetermined relation to the pattern profile a predetermined fluid flow exists through the pilot valve and when the tracer and pattern profile depart in either direction from predetermined relation said fluid flow is gradually diminished as distinguished from known pilot valves which in neutral position inhibit the flow of fluid therethrough and upon departure from neutral in either direction allow the fluid flow or pressure to increase to a maximum.

2. The combination of claim 1 wherein the said pilot valve includes means for varying the rate of fluid flow therethrough for said predetermined relation,

3. The combination of claim 1 wherein the said pilot valve is provided with a plurality of concentric grooves over its bearing surfaces to vent lateral thrust due to fluid pressure.

positioned by said means and controlling a fluid flow, said pilot valve so constructed that when the tracer is in a predetermined relation to the pattern proflle a predetermined fluid flow exists through the pilot valve and when the tracer and pattern profile depart in either direction from predetermined relation said fluid flow is gradually diminished as distinguished from known pilot valves which in neutral position inhibit the flow of fluid therethrough and upon departure from neutral in either direction allow the fluid flow or pressure to increase to a maximum and wherein the said pilot valve is provided with a plurality of concentric grooves over its bearing surfaces to prevent lateral thrust due to fluid pressure.

5. In a machine to0l control, a tracer mechanism for producing a pneumatic pressure'eifect corresponding to a pattern, means sensitive to said pressure effect and having a movable portion, and a pilot valve positioned by-said movable portion and controlling a fluid flow, said pilot valve so constructed that when the tracer is ina predetermined relation to the pattern proflle a predetermined fluid flow exists through the pilot valve and-when the pattern and tracer profile depart in either direction from predetermined relation said fluid flow is gradually diminished.

6. The combination of claim 5 wherein the said pilot valve includes manually positionable means for varying the basic rate of fluid flow through the pilot valve for the said predetermined relation.

7. Control apparatus for relatively moving the tool and workpiece oia material forming or working machine comprising, pattern controlled pneumatic pressure means, separate hydraulic motive means for relatively positioning the tool and work piece along two angularly related paths respectively, the speed oi! movement or the motive means causing movement along one of the two paths being dependent upon the rate of hydraulic fluid passage to or from the said motive means, a variable fluid resistance regulating the rate of hydraulic fluid passage mentioned, and a fluid pilot valve controlling the other motive means. the resistance and the pilot valve Jointly controlled by said pneumatic pressure means.

CLARENCE JOHNSON. 

